Control mechanism for the transmission of a milling machine



Sept. 15 1936. 2,054,165

CONTROL MECHANISM FOR THE TRANSMISSION OF A MILLING MACHINE L. F. NENNINGER ET'AL 7 Sheets-Sheet l Filed Nov. 13, 1931 dwnztt P 1936- F. NENNINGER ET AL 2,054,165

CONTROL MECHANISM FOR THE TRANSMISSION OF A MILLING MACHINE Filed Nov. 15, 1931 7 Sheets-Sheet 2 gwuento'a wwm Sept. 15, 1936.

L. F. NENNINGER ET AL CONTROL MECHANISM FOR THE TRANSMISSION OF A MILLING MACHINE Filed Nov. 13, 1931 7 Sheets-Sheet 3 Sept. 15, 1936- L. F. NENNINGER ET AL 2,054,165

CONTROL MECHANISM FOR THE TRANSMISSION OF A MILLING MACHINE I Filed Nov. 15, 1931 7 Sheets-Sheet 4 gwuentoz attozneq Sept. 15, 1936. F. NENNINGER ET AL CONTROL MECHANISM FOR THE TRANSMISSION OF A MILLING MACHINE Filed- Nov. 13, 1931 7 Sheets-Sheet 5 Sept. 15, 1936. NENNlNGER ET AL 2,054,165

CONTROL MECHANISM FOR THE TRANSMISSION OF A MILLING MACHINE Filed Nov. 13, 1931 '7 Sheets-Sheet 6 Bummer A5575? F Nawmvaae 1w 559N420 jw m/ uric rncg Septl 1936- L. F. NENNINGER ET AL ,0

CONTROL MECHANISM FOR THE TRANSMISSION OF A MILLING MACHINE Filed Nov. 13, 1931 7 s heets -sheet 7 I auozmq Patented Sept. 15, 1936 PATENT OFFICE CONTROL MECHANISM FOR THE TRANS- llflSSION OF A IVIILLING MACHINE Lester F. Nenninger and Bernard Sassen, Cincinnati, Ohio, assignors to The Cincinnati Milling Machine Company, Cincinnati, Ohio, a corpo-.

ration of Ohio Application November 13, 1931, Serial No. 574,800

12 Claims This invention relates to milling machines and more particularly to improvements in the transmission control mechanisms thereof.

One of the principal objects of this invention is to minimize the amount of efiort required on the part of the operator to shift the various con-- trol levers and trip members of a milling machine.

Another object of this invention is to improve the operation'of milling machines by so contriving the control mechanism which determines the relative movement between the work and cutter that the movement of any control lever as when effecting a. change in rate or direction may be completed irrespective of whether the particular clutch shifted thereby has .completed its movement or not.

A further object of this invention is to provide power means under dog or manual control for shifting the various rate and direction determining clutches of a. machine tool thereby simplifying the control mechanism to the end that lighter construction may be utilized in its manufacture.

A still further object of this invention is to provide improved overload or torque limiting devices for the various/rate and direction determining means for the movable parts of a milling machine so that the yielding or slip point of each clutch may be of different value for each support. I

Other objects and advantages of the present invention should be readily .apparent by reference to the following specification considered in conjunction with the accompanying drawings i1- lustrative' of one embodiment thereof but it will be understood that any modifications may be made in the specific structural details hereinafter disclosed within the scope of .the appended claims without departing from or exceeding the spirit of the invention.

Referring to the drawings in which like reference numerals indicate like parts:

Figure l is an elevation of a milling machine embodying the principles of this invention.

Figure 2 is a section on the line 2-2 of Figure 8.

Figure 3 is a section on the line 3-3 of Figure 2.

Figure 4 is a fragmentary-view partly in section as viewed on the line 44 of Figure 2.

Figure 5 is a detail end view of the rate determining clutch control valve as viewed on line 5-5 of Figure 2.

Figure 6 is an expanded view of the variable feed transmission for the work support members.

Figure '7 is an expanded view of the branch transmissions to the different support members.

Figure 8 is a detailed view of the operating cylinder for the rate determining clutch.

Figure 9 is a horizontal section through the knee showing the knee and saddle control mechanisms.

' Figure 1-0 is .an enlarged view of the safety or torquelimiting clutch utilized in the feed transmission.

Figure 11 is a detail view of the table contro mechanism.

Figure 12 is an elevation of the work support with parts broken away to show the control mechanism.

Figure 13 is a detail section on the line l3l3 of Figure 12.

Figure 14 is a diagrammatic view of the work support-transmission and control mechanism.

Figure 15 is an enlarged detail view on the line I 5-]5'01 Figure 12.

Figure 16 is a detail view 1. the line |s-|s of Figure 12.

Figure 16A is a modified form of table control mechanism. 7

Figure 1'7 is a. section on the line l'|l1 of Figure 16A. 7

Figure 18 is a detail showing the table control lever and operating dogs therefor.

Figure 19 is a section on the line l9-l9 of Figure 9.

Figure 20 is a section on the line 2020 of Figure 9. r

Figure 21 is a section on the line 2I-2l of Figure 12. 1 a

In the drawings the reference numeral In indicates the column of a milling machine having vertical guideways ll formed upon one face thereof for reciprocably mounting thereon a knee l2 which carries for cross adjustment a saddle I3, the saddle in turn supporting a table I4 for reciprocating movement laterally of the saddle movement. The column also has journaled in the upper part thereof a spindle l5 for driving an arbor l6 upon-which is secured a cutter I! for operating upon work carried by the table. An overarm I8 is adjustably mounted on the column for supporting the outboard end of the arbor I6 through the medium of a pendant l9. These parts constitute the well known elements of a knee and column type milling machine.

The knee, saddle and table of thistype of machine may be power actuated relative to the cutter and to each other in opposite directions and at diifere'nt rates. a transmission is provided, such as shown in expanded view in Figure 6, which is actuated by a-prime mover 29 located in the,base of 'the column. A

power transmitting band 2| connects the pulley 22 of the motor with the pulley 23- secured to the. end of the main drive shaft 24'. having a gear 25' secured to the end thereof which is continuously driven during operation of the prime mover. This gear, through the gear coup1et'26, actuates the a spur gear 21 keyed to the shaft 28 which also has keyed thereon a pinion 29 meshingwith the gear 38-secured to the primary shaft 3! of the variable,

feed transmission. l

The gear 21 also actuates a rapid traverse transmission comprising a final driver 32 and the interposed gear train 33, 34, 35. I

The variable feed transmission comprises the gear couplets 36 and 31 splined on the, shaft 3| for constant rotation thereby, the couplet 39 including the gears 38 and 39 shiftable into'mesh with the gears 39 and ti respectively, while the couplet 31 has the gears 42 and 43 shiftable into mesh with the gears 44 and 98 respectively. These driven gears are all secured to a parallel shaft 46 which also has fixed therewith another gear 41 with which meshes the gear 48 of the couplet 59 slidably mounted on shaft 5|, the other-- gear 49 of the couplet meshing with the gear ii on the shaft 46. By means of the three shiftable couplets thus far described, the shaft 5| may be rotated at any one. of eight different speeds. A

fourth shaft 52 is journaled in the column par allel to the shaft 5i and has another shiftable gear couplet 53, comprising the gears-54 and 95.: which are shiftable into mesh respectively, with the gears 56 and 61 fixed on the shaft 6|. The shaft 52 also has fixed thereon a gear 58 meshing with the final element 59 of the feed trans-1T mission. The member 59 is a safety gear for permitting slippage incase of extreme overload to thereby prevent breakage of the parts. This safety gear has clutch teeth 60 formed on one face thereof and is mounted for free rotation on: a sleeve Iii-which isjournaled on a shaft. 62

having fixed to one end a bevel gear 63 and splined thereon intermediate of its length a clutch spool 64. v

The gear 32 constitutes the exterior-driving member of a friction disk clutch 65 having pivoted levers 66 adapted to effect engagement of the clutch upon movement of the clutch spool .64 v

to the ,left and thereby rotate the shaft 62 at a rapid traverse rate. Clutch spool 64 is also provided with clutch teeth 61 adapted to engage the clutch teeth 69 of the safety gear to thereby effect rotation of the shaft 62 at any one of the sixteen feed rates of which the feed transmission is capable. j v

As more particularly shown in Figure 7, the bevel gear 63 meshes with a bevel gear 68 secured to the end of a splined shaft 69 which is journaled in the column against axial movement to any one of the'three branch transmissions in the knee and the corresponding support coupled therewith.

' good es I I I 'For, the actuation of these transmissions a drive train is provided comprising-a spur gear 'I2,,in

mesh with thegear 1o, keyed .to the shim; 13,-"

having a bevel gear "H secured to the end thereofin meshwith a bevel gear 15- fixed to the end of a horizontal shaft 18.. This shaft is coupled to a parallel shaft 11 by means of a pinion" and spur gear '19. The shaft TI is splined forslidably receiving the bevel gear 89 meshing with the bevel gear 8| secured to the end of theshaft 82 which comprises a branch transmission for actuating thetable. Atable. reverser is interposed between the shaft 82 and the table feed screw 83 including the bevel gear 84 keyed to the shaft 82'and the bevel gears 85 and 86 mounted for free rotation on-the shaft 83 and theclutch -8 shiftable between these bevel gearsi for-coupling one orthe other to the feed screwin the'usual manner of such reversers. v

The gearl9 alsogacts asa-c'ommon driverfor the branch'transmissions tothesaddle and knee and for this purpose .is in constant mesh with-;a' wide faced pinion 88 which meshes directly with v the gear 89 for effectingrotation thereofin one direction and indirectly with gear 99 through idler 9l for effecting rotation inthe opposite direction, (these two gears 89 and 99 being mountedfor free rotation on the saddle feed shaft 92.- A revers- [ing clutch 93 is shiftably mounted between these gearsfor determining the direction of movement of thesaddle in the well-known manner.

The gears .89 and 99 mesh respectively with tationon an adiacent parallel shaft 96. A'clutch member 91 is interposed between these gears in driving relation with the shaft 96 for effecting movement-of the knee in opposite directions. The-shaft 96 has abevel gear 98 secured to the V fendthereof in mesh with the bevelgear 99 keyed to the upper end of the knee elevating screw 1 90.

" gears 94 and which are mounted for free ro ,1 From the precedingdescription-it should now be apparent that a milling machine ha's been provided havingthreel movable supp rts .in the form of a saddle table and knee together with powerv transmission for eflecting actuation of these supportsatzvariable feed rates ;or. at a rapid traverse rate, and in either one of two directions, the determination of the rate for the three supports belng under the control of a singleclutch, while individual clutches have been provided for determining the directional movement of each supp rt It is well known in clutches that the amount of energy necessary to effect disengagement thereof depends upon the friction between. engaging faces which varies with the amount of power being transmitted by the clutch. In 'a milling machine of the type under discussion this amount is sufiicient to re- V I quire the use of control mechanism having a certain mechanical advantage in order that they may be' conveniently operated manually. Since {the shifting er tooth type.

considerable stress therefore is put-upon'the parts to effect the shifting movements it is apparent that-they must be of sturdy construction. It is desirable therefore that the various clutches be shifted by more direct and powerful means so that the control mechanism may be of lighter construction and the friction losses eliminated, thereby reducing the amount of power necessary to operate the machine.

In the present invention this has been accomplished by providing an auxiliary or intermediate power means which'is directly coupled to the clutch, and which may be controlled by simple mechanism. Preferably this power means is of the hydraulic type as certain advantages result from its use due to the inherent qualities of this medium. For instance, the hydraulic pressure may be put under the control of a valve and the operating lever therefore may be moved immediately to an open or closed'position by the operator without the necessity of waiting for the clutch teeth to interengage or mesh. with one another such as would be necessary if the clutch was shifted through mechanical means as is usual in present construction.

With the shifting of the clutch under the control of a valve, the amount of energy or power necessary to turn the valve remains the same irrespective of the load being transmitted by the clutch and does not increase withthe load being transmitted. The control mechanism may therefore be made of lighter construction which is more easily operated.

To further facilitate the shifting of the clutches and reduce the accompanying friction losses the clutch teeth IOI of the present invention have been beveled or inclined as is shown in Figure 10, which thereby reduces the amount of possible abutting areas tending to present engagement to a minimum. The bevel of these teeth may be made sharp thereby permitting greater friction to be created between the teeth which decreases the possibility of slippage or they may be made with a greater included angle approaching the flat which increases the possibility of slippage. In this manner the overload capacity of a clutch may be varied, and'the clutches for the various supports may be different if it is desired that each support have a different overload or slippage point.

Referring to Figures 7 and 9 the reversal clutch 91 for the knee is provided with an annular groove I02 for receiving a shifter fork I03 secured to a piston rod I04 which is provided with sleeves I05 upon opposite ends, which are reciprocally mounted in cylinders I06 and I06 formed in the support casting. The sleeves are capable 'of independent movement relative to the pistons and are provided with shoulders I01 which engage the cylinder heads while their ends engage opposite sides ofthe shifter fork so that upon the admission of fluid pressure to both cylinders the clutch member 91 will be moved to a neutral or non-power transmitting position. Upon the release of pressure from one cylinder and the admission of pressure to the other, the clutch 91 will be shifted either into engagement with the gear 94 or the gear to eflfect power'traverse of the knee. This is effected by the hydraulic medium in the pressure cylinder acting on the end of the piston rod, causing it to move inde-' pendent of the sleeve.

Fluid pressure is supplied to these cylinders from a plunger pump I08 located in the lower part of the knee, the plunger I00 of which is actuated by an eccentric I09 formed on the periphery of the gear I9 as shown in Figure 7. Since the gear 19 is constantly driven from the prime mover of the machine it will be apparent that fluid pressure is available at all times for power shifting of the clutches during operation of the machine. The pump I08 is provided with a suitable intake for withdrawing oil from a reservoir in the base of the knee and also with an outlet IIO which is connected by a suitable channel means III with a control valve II2.

This valve comprises a rotatable cylindrical member II3, having a pair of longitudinal bores .A pair of radial ports I2I and I22 formed in the member II3 intersect the bore H5 and when as shown in Figures 19 .and 20 these ports are simultaneously connected with the channels H9 and I20 through ports 9' and I20 formed in the sleeve, the'fluid pressurewill move clutch 91 to a neutral or non-power transmitting position.

The bushing has a port I23 formed in the annular groove I II but angularly displaced from the port I I9 and aport I24 formed in the annular groove I I8 whereby upon rotation of the member II3 through a pre-determined angle to cause the port I2I to register with, the port I23, fluid pressure will flow to cylinder I06, while the cylinder I06 will be connected through port I 24 with the bore I I4 which is open at the end as previously explained, permitting the fluid to return to reservoir at the base of the knee. Movement of the valve II3 counter-clockwise through a 'predetermined angle will connect the port I22 with port I22 in the annular groove H8 and simultaneously connect the groove I" through ports I2I and I 24 with the channel II4 thereby causing the clutch 91 to be moved in .the opposite direction to cause reverse movement of the knee. The valve H3 is provided on the end with a ing I26 in which is secured a handle I2I for manual operation of the valve. A T slotted mem ber I28 is secured to the side of the column to which trip dogs I28 may be secured for cooperation with the lug I26 to rotate the valve to neutral position and thereby limit upward or downward movement of the knee.

A shifter rod I29 is reciprocably mounted in the knee and provided with rack teeth I30 on one end engaging pinion teeth formed in the periphery of the member II 3 and rack teeth I32 in the other end engaging pinion teeth I33 formed on the periphery of the shaft I34 which is journaled'in the front of the knee and provided with operating lever I35 on one end. This linkage makes it possible to actuate the valve II3 from the operators normal position at the front or rear of the machine. Suitable detent mechanism is provided for maintaining the levers in their various operating and neutral positions.

From the foregoing description it should now be apparent that the direction determining or reverser clutch for the knee is shifted by intermediate power means, which in the present instance is hydraulic, under the control of manual or dog actuated levers, the manual control being operable from either the front of the machine or from the side of the machine. It will be noted that the control levers may be immediately shifted to any one of its positions irrespective of whether the clutch controlled thereby has become engaged or not.

The saddle is provided with similar means for shifting its direction determining clutch 93 and includes a shifter fork I36 mounted upon doubleended piston I31 which is reciprocably mounted at opposite ends in cylinders I38 and I39. The admission of fluid pressure to these cylinders is controlled by the valve I40, which is similar in construction and operation to the control valve for the knee and its description therefore need not be repeated. The valve is provided with a rotatable member I4I which as shown in Figure 9 is provided with pinion teeth I42 engaging a rack plunger I43 reciprocably mounted in the knee casting adjacent the under side of the saddle for engagement by trip dogs carried thereby. The valve may thus be moved to neutral position by dogs carried by the saddle to terminate the movement of the same.

The valve is further provided with'pinion teeth I44 formed on the opposite end thereof in engagement with rack teeth I45 formed in the periphery of the shifter rod I46 which is slidably mounted in opposite ends of the knee. The rod I46 is provided at one end with rack teeth I41 engaging rack teeth I48 formed on the periphery of the rotatable shaft I49 which extends through the wall of the knee at one side to receive an operating lever I50. The rod I46 is further provided with a socket I5I which is engaged by a lug I52 integral with the rotatable shaft I53 which extends across the knee and provided on the opposite end with a beveled gear I54 meshing with beveled gear I55 secured to the lower end of stub shaft I56. This shaft is journaled in a projection I51 on the side of the knee and provided on the upper end thereof with a manual control lever I58 whereby the operator may control saddle movement from his position at the side of the machine.

For various operating reasons it is not desirable to power actuate the saddle and the knee simultaneously and therefore to prevent accidental engagement of both the saddle and knee clutches, inter-locking means have been provided comprising a ball I59 which is mounted in a recess between the control shafts I49 and I34 each shaft having an indent therein which is opposite to the ball I59 when the controlling shafts are in neutral position. Upon movement of one shaft or the other to a power transmitting position, the ball will be moved into the indent of the other control shaft thereby preventing its movement until the previous lever is returned to neutral position.

Hydraulic pressure is supplied to the control valve I of the saddle through the flexible chantable control valve is returned to the reservoir.

in the knee. It will thus be seen that the saddle movement may be manually controlled from the front or rear of the machine as well as automatically controlled by dogs mounted on the saddle and that the saddle control valve is in series with the table control valve whereby pressure from the pump passes to the saddle control valve and then to the table control valve, returning in the same order to reservoir.

The directional movements of the table are controlled by the previously mentioned valve I64 which is similar in construction to the saddle and knee control valves and comprises a rotatable member I86 to which are connected the flexible conductors I63 and I65 as previously explained. The member I66 is provided with a segmental gear portion I61, Figure 11, which engages a similar segmental gear I68 keyed to the end of a rotatable and reciprocable control plunger I69. Rotation of the plunger I69 will cause rotation of the valve member I66 and thereby a change in direction in the movement of the table. The valve and the plunger have a neutral positionin which the table is stopped. A detent mechanism has been provided for holding the plunger in any one of three positions and as shown in Figure 15 comprises the member I10 having three indents I1I, I12 and I13 engageable by the spring pressed detent I14 pivotally mounted upon a fixed pin I15. The control plunger is provided with a projecting ear I16 which is engageable bysuitable dogs I11 and I18 mounted in T-slots on the forward edge of the table for rotating the plunger from either power transmitting position to a neutral position.

As previously mentioned the plunger I69 is reciprocable and this is for the purpose of controlling a rate determining clutch whereby the rapid traverse or vice versa. Upon vertical movement of the plunger a second member I19 carried thereby is moved to a position opposite the detent I14. This member, unlike the member I10, is provided with only two indents I and I8I whereby the plunger upon suflicient dog rotation to cause the detent I 14 to ride over the peak I82 between the indents will be flred to effect reversal in the table movement. This acts as a load and fire mechanism for automatically reversing the table. The control plunger may also be moved up or down or rotated manually by the control lever I83 which is mounted for universal movement in the wall of the saddle and provided with a ball shaped end I 84 engaging a similarly formed socket I85 formed in the plunger. I The direction determining clutch 81for the table is provided with a shifter fork I86 mounted intermediate the ends of the piston I81 which is reciprocable in closed cylinders I88 and I89 formed on the saddle casting and connected to the control valve I64 through flexible channels I90 and I9I 4 The control valve I64 may also be rotated from the rear of the machine by means of a control lever I92 which is pivotally mounted to the under side of the saddle and provided with lug I93 engaging a socket I94 formed in the periphery of the reciprocating control rod I95 which is operably connected at the other end through crank mechanism I96 with the member I66.

From the foregoing it will be seen that the table may be manually controlled from either the front or rear of the machine as well as automatigally controlled from trip dogs mounted on the The rate determining clutch 64 previously referred to .as mounted in the columnis hydraulically shifted in a manner similar to that described in connection with the other clutches and includes a shifter fork I91, Figure 8, flxed intermediate the ends of the piston rod I98 which is reciprocably mounted at opposite ends in cylinders I99 and 200. The control valve 20I is provided for this clutch and is connected to the cylinders through channels 202. This control valve is adapted to be automatically actuated from trip dogs "carried by the table and to this end the rotatable member 203 of the valve 20I is provided with a beveled gear segment 204 shown more particularly in Figure 5 for engagement with bevel gear 205 keyed to the end of the vertical rotatable shaft 206. This shaft extends parallel to the side of the column and at the lower end is splined in a pinion gear 201 carried by the I knee meshing with teeth on the rack bar 208 which also engages pinion 209 on the end of the horizontal shaft 2 I 0. The shaft 2I0 is telescopingly splined to the shaft 2| I which is journaled in the forward part of the saddle and fixed against iongitudinal movement relative thereto. A pinion 2I2 mounted on the shaft 2 engages rack teeth 2 I3 (Figure 12) formed in a reciprocating plunger 2 I4 the upper end of which is provided with rack teeth 2 I 5 engaging pinion teeth 2I6 formed on the rotatable shaft 2" the other end of which is provided with similar pinion teeth 2 I 8 as shown in Figure 13 engaging rack teeth 2I9 formed on the plunger I69. The plunger 2 projects above the top of the saddle and is adapted to be engaged by a suitable dog 220 carried on the front edge of the table for depressing the plunger to effect dis-engagement of the rate clutch upon movement of the table to an extreme position thereby preventing damage or breakage of the operating parts. The connecting mechanism just described makes it possible for the plunger I69 to operate the rate determining control valve in the column from dogs 22I and 222 carried by the table. Detent mechanism'has also been provided for the rate determining clutch and comprises a spring pressed detent 223 as shown in Figure 21 engageable with indents 232 and 233 formed in the periphery of the member 234 secured to the shaft 2I1.

The shaft 2| I -is extended to the forward side of the saddle and provided with a lever 226 whereby the rate determining clutch may be shifted manually.

In order that the manual shifting of lever 226 may be performed when the plunger I69 is in neutral and the table stopped, as for instance when imparting rapid traverse to the saddle or knee, lost motion is provided between the pinion 2I2 and its shaft and the shaft 206 is provided with an arm 224 whereby a. spring 225 acting on the arm will normally maintain the valve 20I in such position that the feed clutch will be engaged. Upon upward movement of the handle, the shaft 2I0 will be rotated without transmittingmotion to the plunger I69 which would be incapable of vertical movement anyway while in a vertical position due to the overlap of the peak I82 on the detent I14. The plunger I 69 when in power transmitting position is still capable of rotating 5:; the pinion 2I2 and shaft 2I I in a counter-clockwise direction and upon return movement of the pinion 2I2, the spring 225 will cause the shaft 2 to follow up.

The rate and direction control valve 20I is sup- 60 plied with fluid pressure from a pump 22! which is operated directly from the shaft 29 as shown in Figure 6. This pump draws fluid from a reservoir 228 located in the lower part of the column and forces it through conduit 229 to the control 65 valve. A shaft 230 is coupled to the end of the control valve and extends across the column and through the opposite wall where it is provided with an operating lever 23I. As shown in Figure 1 this permits the operator to directly control the 70 rate and direction clutch from that side of the machine.

A modified form of the invention is shown in Figures 16A, 17 and 18 in which a separate direction control for the table is shown for'use-in 0 tool room machines where reciprocating cycles in which the control levers may be easily and 10 quickly moved from one position to another by intermediate power means under either manual or dog operated control means and the mechanism is so contrived that the movement of these levers may be completed irrespective of whether 15 the clutch controlled thereby has completed its movement or'not. It will also be noted that the rate and direction determining clutch in the column is shiftable by hydraulic means which is under the control of mechanical mechanism car- 20 ried by the saddle for manual or dog operation from the table. It will also be noted that means I have been provided on the table for operating this mechanism to automatically shift the rate determining clutch from rapid traverse to feed in 25 case the table has reached the end of its travel unobserved by the operator thereby acting as a safety feature and reducing possible damage to the parts.

That which is claimed is: 30

1. A milling machine having a column, a cutter spindle rotatably mounted on the column, a work support including a saddle and table adjustably mounted on the column for movement relative to the spindle, a prime mover, a feed transmission 35 and a rapid traverse transmission actuated by said prime mover, a rate determining clutch for coupling the table with either the feed transmission or the rapid traverse transmission, hydrauli-- cally actuated means for shifting said rate detero mining clutch, said clutch being mounted in the column of the machine and means carried by the saddle under control of trip dogs mounted on the table for controlling the operation of said hydraulically actuated means and thereby the rate 5 of movement of the table.

2. In a milling machine having a movable work support, the combination of transmission mechanism therefor including feed and rapid traverse clutch elements, and a clutch member shiftable in the one direction to engage said feed element and in the other direction to engage said rapid traverse element, said feed element being actuated by a safety gear, hydraulic means for shifting said clutch element, trip controlled means therefor including a plunger having a feed position and a rapid traverse position corresponding to the positions of the clutch, means actuated by the clutch element to efl'ect translation of the work support including a table feed screw and nut, and trip means carried by the table and actuable when the feed nut has reached the limit of travel in either direction relative to the feed screw to move the plunger and thereby the clutch to a feed position whereby slippage will take place in the safety gear to prevent damage to the table translating elements.

3. A milling machine having a movable sup .port, power transmission means for actuating said support including independent rate and direction determining clutches, hydraulic means for shifting said clutches including rate and direction control valves, a control plunger capable of axial and rotative movement, motion transmitting means coupling said plunger with one of said valves for actuation thereby upon axial 'movement of the plunger, additional motion transmit= ting means coupling the "plunger with-the other valve for actuation thereby upon rotative move ment of the plunger, diflerent dogs carried by the support for automatically efiecting diflerent of said movements and loadandflre mechanism associated with the control 1 plunger to insure completion of initiated movement' th'ereof by the d e -y '4. A milling machinehaving a column, a knee mounted on the column for vertical movement relative thereto, a saddle movable on the knee toward and from the column, a table reciprocably mounted on the saddle, a power operated member' Joumaled in the knee, branch transmissions extending from said member to each support for actuation thereof, a control clutch in each branch transmission, hydraulically actuated means for shifting said clutches, a pump located in the base of the knee and actuated by said'power member' ior supplying hydraulic pressure and control means for determining the coupling of pressure to said hydraulically actuated means and thereby the member to be moved;

5. A milling machine having a column, a work support mounted on the column for movement relative thereto,'a prime mover mounted in the column, a feed transmission and a rapid traverse transmission actuated by the prime mover and terminating in clutch elements, a rate determiningclutch journaled in the column for selective coupling with said clutch elements, power transmitting'mea'ns coupling the rate clutch with said movable support for power actuation thereby, hydraulically actuated means for shifting said clutch, a pump mounted in the column and actuated by said prime mover for supplying fluid pressure to said hydraulically actuated means and means adjacent the .work support for determining the coupling of pressure to the hydraulically actuated means and thereby the rate or movement of the support f i 1 6. A milling machine having a column, a knee,

saddle and table mounted on the column', for

movement relative thereto and with respect to each other, means for eifecting said movement including a prime mfovermounted in the column,

, a ,feed and rapid traverse transmission actuated thereby, said transmission terminating in clutch elements, a clutch member journaled in the colman in, interposed relation with said elements I for selective coupling therewith to determine the, rateoi movement-or themovable supports, hy-

draulic means for shifting said clutch,'.'a control valve. for determining the coupling of said hydraulic means, a control lever mounted on the 1 knee and directly coupled to said valve for manualactuation thereof, trip control means adja- 'centsaid table for actuating said control valve, and a 'lojst'motion connection between the trip control means and the manual means whereby themanual means may be operated without disturbing the position oi the trip control means.

,tablepa member for supporting the work table 7" A-jmilling machine having a column', a work on'the column for movement relative thereto, a prime mover mounted in the column, means for coupling the prime mover to the table for actuation thereby-including a variable feed transmission and rapid traverse transmission mount-1 ed in the column, a final support actuating means; a' feed-rapid traverse clutch selectively shiftable to connect the transmissions to the final actuating means, fluid operable means for shifting said her driven by the final actuatlngmeans ior sup 1 plying pressure to, the reverser clutch. operating means, a control valve therefor, and trip mechanism carried by the support in operative relation to the table for automatically positioning both of said control valves. g 5 i f 8. In a milling machine the combination with .a movable support 01' power actuated transmis clutch, means actuated by the prime mover ror supplying fluid pressure thereto, a valveitor con-f shifting said clutch, means in the supportgmem sion means for moving said support including 'a each clutch, a common control member operatively connected to'each valve and movable in,- one'plane to position one valve and in a diflerent I plane to position the other valve l 1 '9. A machine tool having-a support, a table carried by the support, a prime mover mounted ftrolling the admission; ofpressureto 'saidufluid actuated means, saidvalve being supported. by; V the column, a reversenclutch. 1n" sene wahane, if

final actuating means, fluid operable meansltor fluid actuated rate determining, ciutchand a, mu I actuated direction determining clutch an inde'-.

pendent source of pressure 'and control valve for 52 0.

in the support, a transmission coupling the prime 1 mover'for, actuation of the table including' 'a twoposition rate determining clutch 'and-a-three position direction determining clutch, apair of I a .30 for shifting the same, a branch-transmission and .fia pump operable thereby for supplying fluidpres fluid operable pistons connected with each clutch sure to said pistons, a threerposition valve for said direction determining clutch, a two 'position valve.

Ior'said rate determiningclutch'; a control, memev her, control connections between each or saidvalves and said member, and a plurality of ditierent' control dogs carried by the table'and etiective on said control member ina different-manher for actuating through the difl'erent control connections the respectively coupled valves for :automatic cyclecontrolfot the table.

' '10. A milling machine having 'a column, a tool mounted in the column, "said trar'ismissio'n'"in transmission actuatedby said shai'tn'a pump for. supplying fluid pressure for said pistons; a three-'- position control valve associated with each pair of pistons and having apressureport connected I with 'said pump, each valve having manually operable means rorshittingthe same to any one? of its three positions, and automatic means individual to the respectivevalves-ror shifting the same from either one or 'two positions to a common third position.

I 11. A milling machinehaving a column, a tool support -joumaled in the column," a. knee, saddle and table carried by the column for adjustment or work in three directions relative to the spindle, a prime mover mounted in the column, a feed transvmission and a rapid traverse transmission continuously actuable by the prime mover and a mounted in the column, said transmission including a final drive shaft extending to the knee,

branch transmissions extending Ironiithe drive shaft to the respective supports and each including a reverser clutch and a pair of fluid operable pistons for shifting the same, an additional branch transmission actuated by said shaft, a pump for supplying fluid pressure to said pistons, a threeposition control valve associated with each pair of pistons and having a pressure port connected with said pump, each valve having a manual control lever positioned for operation from the front of the machine and a second manually operable lever located for operation at the rear of the machine, control connections between each lever and it respective valve for shifting the same from any one of its three positions to any other of said positions, and individual trip operable means associated with each support f; shifting its respective control valve from either one of two operating positions to a common third or stop position.

12. A milling machine having a column, a tool support journaled in the column, a knee, saddle and table carried by the column for adjustment of work in three directions relative to the spindle, a prime mover mounted in the column, a feed transmission and a rapid traverse transmission continuously actuable by the prime mover and mounted in the column, said transmission including a final drive shaft extending to the knee,

branch transmissions extending from the drive shaftto the respective supports and each including a reverser clutch and a pair of fluid operable pistons for shifting the same, an additional branch transmission actuated by said shaft, a pump for supplying fluid pressure for said pistons, a threeposition control valve associated with each pair of pistons and having a pressure port connected with said pump, each valve having a manual control lever positioned for operation from the front of the machine and a second manually operable lever located for operation at the rear of the machine, control connections between each lever and its respective valve for shifting the same from any one of its three positions to any other of said positions, individual trip operable means associated with each support for shifting its respective control valve from either one of two operating positions to a common third or stop position, and means associated with one of said supports selectively positionable to cause said automatic means to shift the valve from either of its two operating positions to a third position to stop support movement, or to shift said valve from one operating position to the other to automatically change the direction of -movement of the support.

LESTER. F. NENNINGER. BERNARD SASSEN. 

